Apparatus for packaging a strand of a flexible material



June 26, 1962 R. HAYDEN ET AL 3,040,999

APPARATUS FOR PACKAGING A STRAND OF A FLEXIBLE MATERIAL Filed July 28, 1958 4 Sheets-Sheet l INVENTOR$ Qaflo 4mm 2066c g wape ATTORNEYS June 26, 1962 R. L. HAYDEN ETAL 3,040,999

APPARATUS FOR PACKAGING A STRAND OF A FLEXIBLE MATERIAL Filed July 28, 1958 4 Sheets-Sheet 2 INVENTORS BY 00e ZZGMe e ATTORNEYS June 26, 1962 R. L. HAYDEN ET AL 3,040,999

APPARATUS FOR PACKAGING A STRAND OF A FLEXIBLE MATERIAL Filed July 28, 1958 4 Sheets-Sheet 3 June 26, 1962 R. L. HAYDEN ET AL 3,040,999

APPARATUS FOR PACKAGING A STRAND OF A FLEXIBLE MATERIAL Filed July 28, 1958 4 Sheets-Sheet 4 INVENT ORS fl J A TTORN E YS trite States 3,040,999 APPARATUS FUR PACKAGING A STRAND OF A FLEXIBLE MATERIAL Ralph L. Hayden and William D. Poole, Vienna, W. Va.,

assignors, by mesne assignments, to Johns-Manville Fiber Glass Ina, Cleveland, Ohio, a corporation of Delaware Filed July 28, 1958, Ser. No. 751,338 Claims. (Cl. 242-43) This invention relates broadly to an improved apparatus for packaging a strand of a flexible material. More particularly, it relates to a novel apparatus for packaging a strand of flexible material on a support in a series of helically inscribed circumferential bights progressing and regressing in spaced relation to form successive layers superimposed in overlapping relation.

Although the apparatus disclosed herein is primarily designed for packaging a strand comprised of a plurality of continuous glass filaments, it is evident that the apparatus is applicable, to the packaging of many flexible materials in strand form.

In the production of a continuous strand comprised of a plurality of line glass filaments, the lineal rate of takeup of the strand upon the support exceeds the lineal rate of descent of the filaments from a bushing or other source, for the purpose of attenuating the filaments to a fine diameter. In the production of strand comprised of very fine glass filaments, the rate of rotation of the package is often approximating a critical range at which it becomes difiicult to consistently produce stable packages free of ringers Without detriment to the integrity of the strand.

Although the traversing mechanism generally operates at a lower tempo than the package support, the operational speed combined with the character of the mechanism often contributes to separation of the filaments, break-outs of individual filaments and fuzzing of the strand, all of which are undesirable.

It is therefore an object of this invention to provide apparatus for high-speed winding of an infinitely continuous strand of a flexible material into a stable package.

Another object of the invention is to provide apparatus for winding a continuous strand onto a support in alternately progressive and regressive layers comprised of a plurality of helical bights.

A further object of the invention is to provide apparatus for winding a continuous strand onto a support in a plurality of layers superimposed in overlapping relation.

A still further object of the invention is to provide apparatus for winding a continuous strand onto a tubular support in a series of spaced helical bights to provide a package that will unwind freely at a uniform tension.

Other objects and advantages of the invention will become more apparent during the course of the following description, when taken in connection with the accompanying drawings.

In the drawings, wherein like numerals are employed to designate like parts throughout the same:

FIG. 1 is an elevation, on a reduced scale, of apparatus for forming a multi-filament glass strand and winding it into a package;

FIG. 2 is an elevation of the package winding apparatus as viewed from the right of FIG. 1;

FIG. 3 is an elevation of one form of the primary traversing mechanism provided by the present invention;

FIG. 4 is a sectional view taken on the line 44 of FIG. 3;

FIG. 5 is an elevation of a modified form of the primary traversing mechanism;

the limits of the reciprocal movement, the strand 12 I FIG. 6 is a sectional view taken on the line 66 of FIG. 5; 7

FIG. 7 is an elevation of another modified form of th primary traversing mechanism;

FIG. 8 is an elevation of the traversing mechanism of FIG. 7 as viewed from-the left; and

FIG. 9 is an elevation of a package diagrammatically indicating the character of the wind.

Referring now to the drawings and particularly to FIG. 1, the numeral 1% generally indicates a bushing or crucible for melting a supply of filament forming glass. The bushing is generally made of pure platinum or platinum alloyed with a heat and corrosion resistant metal such as rhodium or may also be made of a suitable refractory material. The bushing is provided with a plurality of filament forming orifices in the bottom wall, as is well known in the art, arranged in any convenient pattern. Heat to melt the glass may be applied to the bushing electrically or by burning a fluid fuel mixture within the confines of a thermally insulated chamber housing the bushing.

When the glass attains the desired drawing viscosity, the relatively small streams of glass 11 gravitating through the orifices are manually collected into a strand 12 which is threaded into translatory engagement with the face of a guide 13 positioned beneath the bushing 10. The strand 12 is then threaded over the face of a primary traversing mechanism 14 and looped around the tubular support 15.

The guide 13 may assume various shapes depending on the character of the strand. The particular guide shown also provides means for applying :a bonding agent, such as an aqueous starch solution, to integrate the strand. The binder may be applied to the guide 13 by a nozzle 16 or any other suitable apparatus. The guide is comprised of a firm, stationary support 17, usually made of metal, covered by an absorbent material 18 such as felt for distributing the bonding agent over the surface of the filaments 11 at the collection point.

The primary traversing mechanism 14, which will be described in detail hereinafter, is mounted for rotation on the output shaft 19 of a motor 20, which motor is supported on a stationary base.

The tubular support 15, which serves as a base for an individual package, is removably mounted for revolution with an expansible mandrel 21, which mandrel is in turn rotated by the output shaft 22 of a second motor 23.

As shown in FIGS. 1 and 2, the motor output shafts 19 and 22 are preferably positioned horizontally in parallel spaced proximity and the motor 23 is mounted on. a rail 24 for reciprocating the package support 15 longitudinally along its aXis in the direction of the arrow When the package support 15 is centered within descending from the guide bisects the traversing mechanism 14 and the tubular package support in a substantially vertical plane. Though the traversing mechanism 14 moves the strand 12 approximately 3 inches along the periphery of the package support 15, the reciprocation of the package support, in the manner disclosed above, superimposes a secondary traversing movement upon the primary traversing movement which increases the span of the total traverse to produce a centrally crowned package 26 approximately 5%." long on an 8" diameter support 15.

Although it is not mandatory to position and rotate the package support 15 and the traversing mechanism 14 in the directions shown in FIG. 2, it is preferred to do so. As viewed from their free ends, the traversing mechanism 14 is rotated in a counter-clockwise direction as indicated by thearrow 27, and the package support mandrel 21 is rotated in a clockwise direction as indicated by the arrow 28. The counter-clockwise direction of rotation of the traversing mechanism 14 corresponds with the descent of the strand 12 to minimize abrasion and separation of the strand by the traversing mechanism 14. The placement of the mandrel 21 and the direction of rotation dictated by that position is selected for convenience in replacing the package supports 15. The forward position of the mandrel 21 shown in FIGS. 1 and 2, is favored over a position displaced to the rear, which would necessitate a counter-clockwise rotation.

One form of the primary traversing mechanism 14 is shown in detail in FIGS. 3 and 4. This mechanism resembles a reel in substantially concentric relation with the output shaft 19 of the motor 20 to which it is sea cured by one or more set screws 29 engaging threads in 'a like number of holes 30 extending through the wall 'of a hub 31. A circular flange 32 is secured in face 'relation to-the hub 31 in any suitable manner, such as by welding, and is concentric with the output shaft 19. A plurality of tie rods 33 extend perpendicular to the face of the flange 32 opposite the hub 31 at equal angular'intervals on a radius approximating half the radius of the flange. A second flange 34 is mounted in similar relation to the other ends of the tie rods 33 so the flanges 32 and 34- are spaced in parallel face relation. Flat head screws 35 recessed in aligned countersunk clearance holes 34' formed in the flanges 32 and 34- from the outer faces engage threads formed in drilled holes 37 entering opposed ends of each rod 33 parallel with its longitudinal axis. Upon rotation of the traversing mechanism, the outer surfaces 38 of the rods 33 generate a minor diameter concentric with the axis of the shaft 19. The generated minor diameter defines the depth at which the strand 12 enters the traversing mechanism 14.

Individual cams, made of bent rods, are attached to the outer surface 38 of each of the tie rods 33 and inclined at an angle of'approximately 45 to the axis of rotation, terminating at the 'innerface of one of the 'flanges 32 or 34 flush with the periphery 39to present -a strand contacting face in radial alignment with its respective .tie rod 33. Three of the cams that consecutively contact thestrand in the order of rotation, respectively designated. by the numerals40, 41 and 42, are attached to theinner face of theflange 32 flush with the major diameter 39 and are individually joined in angular alignment toa'corresporiding tie'rod 33 so that the strand contacting faces progressively advance toward the opposed flange 34 at regularly spaced intervals with a portion of each cam Tsurface adjacent the-minor diameter in rotationally overlappingrelation toiaportionof the surface of a succeeding cam surface adjacent the major diameter. Therefore, the

strandcontacting surfaces of the earns 40, 41 and42 lie within a 120 sector, however, upon rotation in the di- Irection previously designated, each cam in recited order contacts thestrand for approximately 60 of arc to progressively move the strand approximately 1" to the right (FIGS; land 3), which direction is away from the flange 32 toward the'flange 34. Collectively, the cams 40, 21

fand42 progressively move the strand approximately 3".

A second series of three cams, respectively identified 'by the numerals '43, 44 and 45, are individual duplicates of thecams 40, '41 and 42 of the first series and are respectively, joined at their termini to the remain ing three tie rods 33 in their rotative order and the inner face of the flange 34' flush with the major diameter 39 and with each cam in angular alignment with its corresponding tie'rod' 33. Thus, the earns 43, -44 and 45 of the second series are within a 120 sector diametrically 4 The cams 43,44 and 45 comprising the second series, progressively movethe strand 12 approximately 3" to the left in-the same manner as the cams 40, 41 and 42 comprising the first series move the strand-a like distance to the right. In other words, as viewed in FIGS. 1 and 3, for each revolution of the traversing mechanism 14, the earns 40, 4 1 and 42 progressively deflect the path of the strand 12 three inches to the right and the cams 43, 44 and 45 progressively deflect the path of the strand 12 three inches to the left, in alternate succession, to superimpose one layer, comprised of a series of circumferential bights 46 (FIG. 9) upon a preceding layer wherein the bights progress in the opposite direction.

When the traversing mechanism 14, as disclosed above, is used in conjunction with an axially reciprocating package support 15, a centrally crowned; package 26 (FIG. 9) comprised of a plurality of layers in overlapping relation is produced with each layer comprised of successive bights 46 of the strand 12 inscribing a helix about the support 15. By rotating the package support 15 at a rate five to eight times greater than the traversing mechanism 14, successive bights 46 comprising each progressively or regressively wound layer will span a little more than oneha-lf the length of the package and, for example, at the aforementioned ratio of 8 to 1, each layer will be comprised of four helical bights 46 in spaced relation as is shown diagrammatically in FIG. 9.

Although it may be advantageous to vary the number of cams within the even number series for other sizes and types of packages, it has been found by experimentation that for the package described above that six cams produce the best results.

The modified form of the traversing mechanism shown in FIGS. 5 and 6 and indicated generally by the numeral 47, is illustrated as being a metal casting, however, it may be constructed of any suitable material and in any manner to attain an identical configurataion. The strand contacting surfaces are highly polished to prevent snagging the strand.

A pair of circular flanges 48 and 49, in spaced relation, peripherally define a major diameter 50 concentric with the output shaft '19 of the motor 20 as disclosed in the first embodiment of this invention. The flanges are joined by a cylindrical hub 51, the outer surface of which defines a minor diameter 52 concentric with the output shaft 19 and equal to the generated minor diameter of the first embodiment.

One of a pair of diametrically opposed cam sectors, indicated by the numeral 53, has a surface 54 inclined at approximately 4 to joint the minor diameter 52with the major diameter 50 of the flange 48. Theinclined surface 54 advances helically within a sector toward the inner face of the flange 49 and is adapted to engage the strand 12 to progressively deflect its translatory path a distance extending approximately 3" to the right as viewed in FIG. 5. The other cam sector 55 has a similarly formed helical surface 56 inclined at approximately a 45 angle in opposition to the surface 54, joining minor diameter 52 to the major diameter 50 of the flange 49. As previously stated, the cam sectors are diametrically opposed and therefore the cam sector 55 advances helically toward the flange 48 within a 120 sector. Both cam sectors 53 and 55 respectively terminate at a point on the minor diameter 52 spaced about one-half inch from the inner surfaces of the flanges 49 and 48.

Though each of the diametrically opposed cam surfaces 54 and 56 subtends an arc of not more than 120, upon rotation of the traversing mechanism 47 in the direction previously specified, each camsurface engages the strand 12 for slightly less than of opposed-halfcycles of the traverser.

A second modified form of the primary traversing mechanism is shown in FIGS. 7 and 8 and is generally indicated by the numeral 57. This form of the invention is similar in construction to the form disclosed in FIGS. Item 4, the main difference being a reduction in tion in the mass. This feature is particularly advantageous when operating within the upper speed ranges.

The traversing mechanism '57 includes an elongated hub 58 comprised of a tube 59 with concentric terminal flanges 60 and 61 only slightlylarger in diameter than the tube 59. The bore 62 of the tube extends through the flanges 60 and 61 and is adapted to receive the shaft 19 of the motor 20 to which it is secured by one or more set screws 63 engaging threads formed in a like number of holes 64 penetrating the wall of the flange 60'.

As in the form of the invention shown in FIGS. 3 and 4, two series, comprised of three cams each, are angularly spaced at 60 intervals around the hub 58 with the cams comprising each series in facial opposition to th cams of the other series. Taken in the order in which the cams successively engage the strand 12, the cams comprising the first series are respectively indicated by the general numerals 65, 66 and 67 and the cams compris ing the second series are respectively indicated by the numerals 68, 69 and 70. Also, as disclosed in relation to the form of the invention shown in FIGS. 3 and 4, each of the cams taken in ascending numerical order includes a strand contacting surface respectively numbered 71, 72, 73, 74, 75 and 76 individually corresponding in all respects to the surfaces of the cams 40, 41, 42, 43, 44 and 45 of FIGS. 3 and 4. In other words, the strand engaging cam surfaces of the tWo forms of the invention shown in FIGS. 3 and 4 and 7 and 8, are positioned in identical relation to the axis of rotation of the traversing mechanism and both bias the strand 12 along the periphery of the package support 15 an equal distance in alternately progressive and regressive motions.

Furthermore, the portion of the cam surfaces remote from the axis of the hub 58 generate a major diameter and the cam surfaces adjacent the axis of the hub 58 generate a minor diameter corresponding respectively to the major and minor diameters generated by the cam surfaces of FIGS. 3 and 4.

The radial extremities of the cams 65, 66 and 67 comprising the first series are respectively extended by legs 77, 78 and 79 paralleling the axis of the hub 58 and then bending at right angles to respectively enter blind holes 80, 81 and 82 entering the periphery of the flange at 60 intervals.

The opposite ends of the cams 65, 66 and 67 comprising the first series are respectively extended from the minor diameter by legs 83, 84 and 85 contacting the periphery of the tube 59 and terminating in holes 86, 87 and 88 penetrating the flange 61 from face to face in angular alignment with the blind holes 80, 81 and 82. The cams are secured by soldering.

The earns 63, 69 arid 70 comprising the second series are respectively identical in configuration to the cams 65, 66 and 67 of the first series, but are reversed so the strand contacting surfaces of the two series are inclined in opposition.

The major diameter extremities of the cams 68, 69 and 70 comprising the second series are respectively extended by legs 89, 90- and 91 parallel-ing the axis of the hub and then bending at right angles to respectively enter blind holes 92, 93 and 94 entering the periphery of the flange 61 at 60 intervals. The :holes 92, 93 and 94 are diametrically opposed to the blind holes 80, 81 and 82.

The opposite ends of the cams 68, 69 and 70 comprising the second series are respectively extended by a leg 95, 96 or 97 in contacting relation to the periphery of the tube 59 with each leg respectively terminating in a hole 98, 99 or 100 penetrating the flange 60 from face to face at points respectively in diametrical opposition to the holes 86, 87 and 88. The cams 68, 69 and 70 are also secured to the hub 58 by soldering.

Substitution of either of the modified traversing mechanisms 47 or 57 for the traversing mechanism 14 will not alter the form of the package 26 or the character of the Wind. Using either embodiment of the invention, the

a speed eight times greater than the traversing mechanism.

14. As an example, by increasing the rotational speed of the traversing mechanism the number of bights 46 in each ayer will increase proportionately and the lead angle of successive bights 46 will decrease proportionately. Conversely, by decreasing the rotational speed of the support with respect to the rotational speed of the traversing mechanism 14 the number of bights 46 in each layer will decrease proportionately and the lead angle of successive bights will increase proportionately.

It is to be understood that the forms of the invention herewith shown and described are to be taken as illustrative embodiments only of the same, and that various changes in the shape, size and arrangement of parts, as well as various procedural changes may be resorted to without departing from the spirit of the invention or the scope of the subjoined claims.

We claim:

1. Apparatus for winding an infinitely continuous strand 7 of .a flexible material upon the periphery of a cylindrical support including a source for supplying said strand, means for rotating said support about an axis remote from said source, a stationary guide intermediate said source and said support to direct said strand onto the periphery of said support in a path that is perpendicular to said axis of rotation, and a traversing mechanism rotating with a centrally related supporting axle disposed parallel and adjacent to said support for moving said strand along the periphery of said support in a cycle including a progressive and regressive motion, said traversing mechanism including a plurality of series of cams with each of the cams being spaced at equal angular intervals, each series generating in each revolution a surface inclined with respect to said axle and opposed to the other surface, and each surface advancing helically at a uniform rate to alternately engage said strand for a period approaching one-half of each cycle and move said strand along the periphery of said support in alternately opposed directions.

2. An apparatus for Winding an infinitely continuous strand of a flexible material upon the periphery to a cylindrical support as defined in claim 1, including means for reciprocating said support longitudinally along its axis.

3. An apparatus for winding an infinitely continuous strand of a flexible material upon the periphery of a cylindrical support including a source for supplying said strand, means for rotating said support about an axis remote from said source, a stationary guide intermediate said source and said support adapted to direct said strand onto the periphery of said support in a path that is perpendicular to said axis, and a traversing mechanism rotating with a centrally related supporting axle disposed parallel and adjacent to said support for moving said strand along the periphery of said support in a cycle including a progressive and a regressive motion, said traversing mechanism comprising two terminal flanges in spaced face relation defining a major diameter concentric with said axle, an even numbered plurality of rods radially spaced at equal angular intervals joining said flanges to define a minor diameter concentric with said axle, and cam means radially aligned with each of said rods and with ordinately successive cams contained within diametrically opposed half sectors inclined to join said minor diameter with the major diameter of opposite flanges, whereby upon rotation said cam means generate a pair of diametrically opposed helically formed surfaces, each in contact with said strand for a period approaching one-half of the said cycle to cyclically deflect said strand so that it is wound upon the periphery of said support in a plurality of alternately progressive and regressive superimposed layers wherein each of said layers is comprised of a series of circumferentially extending helical bights.

4. The apparatus as defined in claim 3, wherein six cams are spaced at 60 intervals and wherein three successive cams taken in the order of rotation form -a first series for progressing said strand along the periphery of said support and the three remaining successive cams taken in the order of rotation form a second series for regressing said strand along the periphery of said support.

5. An apparatus for winding an infinitely continuous strand of a flexible material upon the periphery of a cylindrical support including a source for supplying said strand, means for rotating said support about arr axis remote from said source, a stationary guide intermediate said source and said support adapted to direct said strand onto the periphery of said support in a path that is perpendicular to said axis, and a traversing mechanism rotating with a centrally related supporting axle disposed parallel and adjacent so said support for moving said strand along the periphery of said support in a cycle including a progressive and a regressive motion, said traversing mechanism comprising an elongated hub concentric with said axle and an even numbered plurality of cams projecting radially from said hub at equal angular intervals in two diarnetricallyopposed series wherein the cams of one series are in inclined facial opposition to the cams of the other series and wherein the generated minor diameter of each cam series terminates in overlapping axial relation adjacent the generated majordiameter of the cam series next in the rotational order of succession.

6. In apparatus for winding an infinitely continuous strand of flexible material about a core support including a source of said strand, means for rotating said support about a first axis, a guide intermediate said source and said support adapted to direct said strand in a path that is substantially perpendicular to said first axis, and a traversing mechanism rotating'about a second axis which is parallel and adjacent to said support for moving said strand along the periphery of said support in a cycle including a progressive and a regressive motion, the improvement wherein said traversing mechanism comprises: a plurality of cams spaced at equal angular intervals about said second axis and forming two series, said series being diametrically opposed, each of said cams having a strand engaging surface which corresponds with the strand engaging surfaces of the ordinately successive cams within a series to define a helical path for said strand which joins the minor diameter of one series with the major diameter of the other series.

7. The apparatus as described in claim 6, wherein each cam defines a radial plane with respect to said second axis.

8, The apparatus as described in claim 6, wherein the strand engaging surface of an individual cam is inclined in only one direction with respect to said second axis.

9. In apparatus for winding an infinitely continuous strand of flexible material about a core support including a source of said strand, means for rotating said support about a first axis, a guide intermediate said source and said support adapted to direct said strand in a path that is substantially perpendicular to said first axis, and a traversing mechanism rotating about a second axis which is parallel and adjacent to said support for moving said strand along the periphery of said support in a cycle including a progressive and a regressive motion, the improvement wherein said traversing mechanism comprises: 6 cams spaced at intervals, 3 of said cams taken in successive order of rotation forming a first series for progressing said strand along the periphery of said support, and the 3 remaining successive cams taken in order of rotation forming a second series for regressing said strands along the periphery of said support.

10. In apparatus for winding a continuous strand of flexible material about a core and including a source of said strand, means for rotating said core about a first axis, and a traversing mechanism rotatable about a second axis parallel to said first axis and adjacent to said core for moving said strand along the periphery of said core in a cycle including a progressive and a regressive motion, the improvement wherein said traversing mechanism comprises: a plurality of cams spaced apart from each other and which when taken in successive order of rotation form a first series for progressing said strand along the periphery of said core; and a plurality of cams spaced apart from each other and which when taken in successive order of rotation form a second series for regressing said strand along the periphery of said core, each of said cams defining a radial plane with respect to said second axis.

References Cited in the file of this patent UNITED STATES PATENTS 1,888,395 Sohweiter Nov. 22, 1932 2,352,781 Fletcher et al. July 4, 1944 2,391,870 Beach Jan. 1, 1946 FOREIGN PATENTS 23 1,800 Germany Mar. 3, 1911 

